Rotary expansible chamber device

ABSTRACT

A rotary engine comprises a block, a plurality of longitudinally extending cylindrical chambers formed in the block, the longitudinal axes of which are in parallel spaced relation, a rotor disposed in each of the longitudinally extending chambers, each of the rotors having a peripheral surface in substantial surface-to-surface contact with the peripheral surface of at least one other of the rotors, intake and exhaust ports formed in the block for communicating the longitudinally extending chambers with sources of combustible materials and an exhaust system, the intake and exhaust ports of each chamber being covered and uncovered by the rotation of the rotor mounted in the respective chamber, means for interengaging the rotors to control the rotation of each relative to the others, ignition means, means for attaching at least one of the rotors to a means to be driven, and relieved portions formed on each of the rotors for cooperating with the longitudinally extending chambers to define working volumes which are displaceable from being in communication with the inlet ports to being in communication with the ignition means and thereafter to being in communication with the exhaust ports during each combustion cycle of the engine.

Feb. 12, 1974 [57] ABSTRACT A rotary engine comprises a block, aplurality of longitudinally extending cylindrical chambers formed in theblock, the longitudinal axes of which are in parallel spaced relation, arotor disposed in each of the longitudinally extending chambers, each ofthe rotors having a peripheral surface in substantial surface-tosurfacecontact with the peripheral surface of at least one other of the rotors,intake and exhaust ports formed in the block for communicating thelongitudi nally extending chambers with sources of combustible materialsand an exhaust system, the intake and exhaust ports of each chamberbeing covered and uncovered by the rotation of the rotor mounted in therespective chamber, means for interengaging the rotors to control therotation of each relative to the others, ignition means, means forattaching at least one of the rotors to a means to be driven, andrelieved portions formed on each of the rotors for cooperating with thelongitudinally extending chambers to define Andrew Takacs, 99 Farm RoadCir., Brunswick, NJ. 08816 Oct. 25, 1972 106,351, Jan. 14, 1971,

References Cited UNITED STATES PATENTS Inventor:

Related US. Application Data [63] Continuation of Ser. No.

abandoned, which is a continuation-in-part of Ser. No. 854,328, Aug. 28,1969.

U.S. Field of Search waited States Patet Takaes ROTARY EXPANSIBLECHAMBER DEVICE [22] Filed:

[21] Appl. No.: 300,652

working volumes which are displaceable from being in communication withthe inlet ports to being in communication with the ignition means andthereafter to being in communication with the exhaust ports during eachcombustion cycle of the engine.

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SHEET UBUF 10 mama] M12 5.791.352 SHHT IUDF 10 ROTARY EXPANSIBLE CHAMBERDEVICE BACKGROUND OF THE INVENTION This application is a continuation ofmy copending continuation-in-part for Rotary Engine, Ser. No. 106,351,filed Jan. 14, 1971, and now abandoned which is a continuation-in-partof my application for ROTARY ENGINES, Serial No. 854,328, filed Aug. 28,1969 and now abandoned. This invention relates generally to expansiblechamber devices and particularly relates to rotary internal combustionengines. This invention further relates to rotary heat engines,compressors, motors and pumps.

Those concerned with the design and development of internal combustionengines long have been interested in the direct conversion of combustionenergy into rotary motion. The single common most important goal ofthose directing their attentions to the development of rotary engineshas been the desire to eliminate, in smaller internal combustionengines, the occurrence of reciprocating parts with their attendantvibration, wear and overall inefficient operation.

The prior art contains much evidence of activity toward the developmentof a commercially feasible rotary engine. The engines resulting fromthis activity, however, have not been sufficiently satisfactory to gaincommercial acceptance. Among the problems experienced by prior artengines has been that the combustion of gases coupled with the additiveeffect of internal engine friction have caused errosion and burning ofthe sealing faces as well as distortion of the engine components andhousing. Additionally, the friction generated by the known arrangementutilized for internal sealing has been sufficiently great to precludehigh speed operations. Finally, the combustion gas-flow characteristicsof many known engine structures have not been adequate for properlyscavenging the exhaust gases, thus reducing the capability of the enginefor charge and therewith the engine efficiency.

SUMMARY OF THE INVENTION Among the objects of the present invention,therefore, are to provide a rotary engine which is subject to lessfrictional heat and wear than known rotary engines, to provide a rotaryengine which can be operated at virtually any speed necessary toaccomplish efficient operation, and to provide a rotary engine having agas flow characteristic which provides for complete scavenging ofexhaust gases thereby increasing the charge of combustible mixture percycle so as to increase the engine efficiency. A further object of thepresent invention is to provide a rotary engine wherein there are noreciprocating parts.

The foregoing representative objects and others not enumerated areaccomplished by the rotary engine of the invention, one embodiment ofwhich may include a block, a plurality of longitudinally extendingcylindrical chambers formed in the block, the longitudinal axis of thelongitudinally extending chambers being in parallel spaced relation,rotatable means disposed in each of the longitudinally extendingchambers, each of the rotatable means having a peripheral surface insubstantial surface-to-surface line contact with the peripheral surfaceof at least one other of the rotatable means, intake and exhaust portsformed in the block and communicating at least one of the chambers withmeans for charging the at least one chamber with a combustible mixtureand an exhaust system, respectively, the intake and exhaust ports foraccommodating the introduction and exhaust of combustion materials andcombustion products into and from their associated chambers, and theintake and exhaust ports being selectively covered and uncovered by therotation of the rotatable means disposed in their respective cylindricalchambers, means for interengaging the rotatable means to control therotation of each of the rotatable means relative to the others, ignitionmeans, at least one relieved portion on the peripheral surface of eachof the rotatable means, the relieved portions cooperating with thelongitudinally extending cylindrical chambers to define working volumes,said working volumes being effectively displaced from being incommunication with the inlet ports to being in communication with theignition means and thereafter to being in communication with the exhaustports during each combustion cycle of the rotary engine, and means forattaching at least one of the rotatable means to a means to be driven.

The rotors and rotor valves have a body of each thickness at theirmating surfaces, which thickness is filling with extremely closeclearance, the thickness of the chamber cavity, with the only exceptionbeing, where either valve(s) or rotor(s), not both, is (are) fitted withrunning middle or side plates in which case the respective chamber has acavity thickness to include such plates, said plates having a completelycircularv curvature and their purpose being mainly to improve coolingarid sealing.

BRIEF DESCRIPTION OF THE DRAWINGS A'more complete understanding of thepresent invention may be had from the following detailed descriptionthereof particularly when read in the light of the accompanyingdrawings, wherein:

FIG. 1 is a partially cross-sectional, cut-away perspective view ofarotary engine according to the invention;

FIG. 2 is a cross-sectional, elevational view of the engine of FIG. 1;

FIG. 3 is a cross-sectional view through the planes 33 of FIG. 2;

FIG. 4 is a cross-sectional, elevational view through the plane 44 ofFIG. 3;

FIGS. 5-40 are schematic views showing, progressively, the operation ofthe engine shown in FIGS. l-4;

FIGS. 1144 are schematiccross-sectional views of engines similar to theengine of FIGS. 11-4 but having provision for three rotors rather thantwo rotors;

FIGS. 15-17 are schematic cross-sectional views of an engine similar tothe engine of FIGS. 11-4 wherein the rotors are provided with singlerelieved surfaces rather than two relieved surfaces;

FIGS. 19-22 are schematic cross-sectional views of an engine accordingto the present invention wherein a single main rotor is utilized incombination with a rotary valve comprising a single rotating lobe; and

FIGS. 23, 24 and 25 show still another embodiment of the presentinvention, similar to the embodiment of FIGS. 19-22, wherein the mainrotor member is generally circular in cross-sectional configuration, thecircle being developed about an axis which is offset from the axis ofrotation of the rotor member.

DETAILED DESCRIPTION Referring to FIG. 1, a rotary engine according tothe invention is shown and designated generally by the reference numeral10.

Engine comprises a block having first and second end elements 12 and 14which are separated by a central element 16, all of the block elementsbeing rigidly secured together by suitable means such as bolts 17.Formed in central block element 16 are upper and lower axially extendingcylindrical chambers 20 and 22, respectively. The longitudinal axes ofchambers 20 and 22 are parallel and lie in a plane which also containsthe longitudinal axis of an intermediate cylindrical chamber 23, whichaxis is parallel to the longitudinal axes of chambers 20 and 22. Thediameter of intermediate chamber 23 is larger than the distance betweenthe peripheries of chambers 20 and 22 thus effecting a communicationbetween chambers 20 and 22 through chamber 23.

The intersection of upper chamber 20 with intermediate chamber 23defines first and second longitudinally extending edges 25 and 26.Similarly, the intersection of intermediate chamber 23 with loweraxially extending chamber 22 defines third and fourth longitudinallyextending edges 27 and 28, respectively.

Operably disposed within upper cylindrical chamber 20 is a first rotor30 which is rigidly mounted by a suitable key means on a shaft 32.Referring to FIGS. 14, it can be seen that shaft 32 extends throughsuitable bores 33 and 34 in first and second block elements 12 and 14,respectively, and is supported for rotation by bearings 37 and 38 whichare rigidly mounted in suitable annular channels 40 and 41 formed inblocks 12 and 14, respectively.

Leakage of fluid into or out of chamber 20 between shaft 32 and bores 33and 34 is prevented by seals 43 and 44 which are of known structure andmounted in suitable annular channels formed in the surfaces of bores 33and 34.

Shaft 32 is relieved at suitable plural positions adjacent its ends todefine radially extending shoulders which are useful in axiallypositioning bearings 37 and 38. The end of shaft 32 adjacent first block12 also is provided with a relieved portion for rigidly receiving apinion gear 46, the function of which is discussed in detail below.Additionally, each end of shaft 32 is provided with a threaded sectionfor securely receiving nuts 48 and 49 which cooperate to secure shaft 32and its related structure in axial position within blocks 12, 14 and 16.

In a manner substantially identical to first rotor 30 in uppercylindrical chamber 20, there is operably disposed within lowercylindrical chamber 22 a second rotor 50 which is rigidly mounted suchas by keying to a shaft 52. AS may be best seen in FIGS. 3, shaft 52extends through suitable bores 54 and 55 in first and second blockelements 12 and 14 respectively and is supported for rotation bybearings 57 and 58 which are rigidly mounted in suitable annularchannels 60 and 61 formed in blocks 12 and 14, respectively.

Leakage of fluid into or out of lower cylindrical chamber 22 between thesurface of shaft 52 and the surfaces of bores 54 and 55 is prevented byseals 63 and 64 which may be any of many known types and which aremounted in suitable annular channels formed in the surfaces of bores 54and 55.

Shaft 52 is relieved at plural positions adjacent its ends to defineradially extending shoulders which are useful in axially positioningbearings 57 and 58. The end of shaft 52 adjacent first block 12 is alsoprovided with a relieved portion for rigidly receiving a gear 66 thefunction of which is discussed below in detail. Additionally, thesurface of shaft 52 adjacent bearing 58 and the surface of shaft 52adjacent gear 66 are each provided with a threaded section for securelyreceiving nuts 68 and 69 which cooperate to secure shaft 52 and itsrelated structure in axial position within blocks 12, 14 and 16.

The end of shaft 52 adjacent first block element 12 extends axially awayfrom block element 12 through a gear cover 71 whereupon it is terminatedwith a splined section 72 adapted for connection to a suitable powertakeoff means. The opposite end of shaft 52, Le. the end adjacent secondblock element 14, extends beyond block 14- and is adapted for suitableconnection to a starter means (not shown), for the engine 10.

Operably disposed within intermediate cylinder 23 is a rotary valve 75comprising a lobe 76 which is rigidly secured such as by keying to ashaft 78. The longitudinal axis of shaft 78 is parallel and in the sameplane with the longitudinal axes of rotors 30 and 50. Additionally,shaft 78 extends through suitable bores 80 and 81 in first and secondblock elements 12 and 14, respectively, and is supported for rotation bybearings 84 and 85 which are rigidly mounted in suitable annularchannels 87 and 88 formed in blocks 12 and 14, respectively.

Leakage of fluid into or out of intermediate chamber 23 between thesurface of shaft 78 and the surfaces of bores 80 and 81 is precluded byseals 90 and 91 which may be any of the known types and as shown aremounted in suitable annular channels formed in the surfaces of bores 80and 81, respectively.

In a manner similar to that discussed above with respect to shafts 32and 52, shaft 78 is relieved at plural positions adjacent its end todefine radially extending shoulders which are useful in axiallypositioning bearings 84 and 85. The end of shaft 78 adjacent first block12 is also provided with a relieved portion for rigidly receiving a gear79, the function of which is discussed in detail below. The axialposition of rotary valve 75 is maintained by nuts 95 and 96 which arethreadedly secured to the ends of shaft 78 and cooperate not only tomaintain shaft 78 and rotary valve 75 in proper axial position but alsoto axially position the related structure such as gear 79.

With particular reference to FIG. 4, it can be seen that gears 46, 66and 79 are operably engaged by first and second idler gears 99 and 100.Specifically, idler gear 99 is in meshed engagement with both pinion 46and with gear 79, and idler gear 100 is in meshed engagement with bothgears 79 and gear 66. Idler gears 99 and 100 are rigidly mounted onshafts 102 and 103. Shaft 102 is mounted for rotation in a first bearing105 which is supported in a suitable annular channel formed in thesurface of first block element 12 and a second bearing 106 which issupported in a suitable bore formed in gear cover 71. Similarly, shaft103 is supported for rotation by a first bearing (not shown) mounted ina suitable annular channel formed in the surface of first block element12 and a second bearing (not shown) which is mounted in a suitable boreformed in gear cover 71. Thus, caps may be provided on cover 71 toinsure that dirt is excluded from bearings 106 and the correspondingbearing for shaft 103 Gears 46, 66, 79, 99 and 100 may be provided withsuitable teeth of any of the known types capable of handling the loadsgenerated by engine 10. With respect to the speed ratios of therespective gears, gears 46 and 66 are equal in effective diameter,whereas in the embodiment shown the effective diameter of gear 79 is onehalf the effective diameters of gears 46 and 66. Thus, the speed ratioof rotation of gears 46 and 66 is 1:1 and the speed ratio of gears 46and 66 to gear 79 is 2:1. Gears 99 and 100 are idler gears and as suchmay be of any suitable diameter.

The central portions of central block elements 16 are relieved to definemounting spaces for first and second spark plugs 109 and 110. Theseplugs extend radially inwardly through suitable bores in central element16 toward the axis of rotation of shaft 78 and their ignition gaps arein communication with the interior of intermediate chamber 23 on opposedsides of rotary valve 75. Each of spark plugs 109 and 110 is actuated bya suitable distributor 1 12 which is operably connected to theelectrical system (not shown) associated with the engine 10. Distributor112 is physically mounted on gear cover 71 and its rotor is driven by agear 114 formed on the outer end of shaft 102 on which idler gear 99 ismounted.

Extending through the walls of central block element 16 and into uppercylindrical chamber are a first bore 116 and a second bore 117. Thefirst bore 116 defines an intake opening which is suitably connectedthrough a fuel mixture line 119 to a suitable carburetor 120 which maybe any of many which are generally known in the art. Second bore 117defines an exhaust passage which is suitably connected to an exhaustline 122 for carrying the exhaust gases from the engine to a suitablemuffler device (not shown).

Disposed generally below exhaust passage 117 is a third bore 124 incentral block element 16, which bore defines an intake passage forcommunicating the interior of lower cylindrical chamber 22 with anintake line 126 extending from carburetor 120. Similarly, disposed underintake passage 116 is a fourth bore 128 which defines an exhaust passagefor communicating the interior of lower cylindrical chamber 22 with anexhaust line 129 which, in a manner similar to exhaust line 122, carriesexhaust gases from the engine to a suitable muffler means.

Formed in the upper surface of upper cylindrical chamber 20 is alongitudinally extending slot 131 in which is slidably received adivider strip 133. Divider strip 133 is urged out of slot 131 by theaction of a spring 134 mounted within the slot behind divider 133. Theinner surface 135 of divider 133 is rounded and adapted forsurface-to-surface engagement with the pe-- ripheral surface of firstrotor 30. The force with which the surface 135 of divider strip 133bears against the surface of first rotor 30 is adjustable by adjusting apair of set screws 136 which establish compressive load on spring 134.The surface of chamber 20 is relieved between slot 131 and bore 117 todefine a channel 137 the purpose of which is discussed below in detail.

Similarly, the lower surface of lowerv cylindrical chamber 22 isprovided with a longitudinally extending slot 139 in which is slidablyreceived a second divider strip 141. A spring 143 is disposed behindsecond divider strip 141 and adjustable by set screws 144 urges dividerstrip 141 out of slot 139 and into engagement with the peripheralsurface of second rotor 50. In this regard, the inner surface of divider141 is also rounded to accommodate the surface-to-surface engagement ofstrip 141 with the surface of rotor 50 during operation of the engine.Slot 139 is in fluid communication with exhaust bore 128 through achannel 145 formed in the surface of chamber 22. As will be discussedbelow during the description of the operation of engine 10, first andsecond divider strips 133 and'141 cooperate with rotors 30 and 50respectively, to define the limits of the intake volumes and exhaustvolumes of upper and lower cylindrical chambers 20 and 22 respectively.

It should be noted that no specific means for cooling engine 10 havebeen disclosed. It will be recognized by those skilled in the art,however, that engine 10 as well as the other embodiments of rotaryengines as described in detail below, depending upon the particular sizeand load characteristics of an engine of this type in use, may be cooledby water systems or air systems or other of the many systems generallyknown in this art. Additionally, engine 10, as well as the other embodiments of rotary engines disclosed, may be fabricated from any of themany known metals which are suitable for use in this art. In thisregard, it should be noted that rotors 30, 50 and lobe 76 are all shapeswhich require no undercut and as such are capable of being manufacturedby basic manufacturing processes and therefore are relativelyinexpensive. Because the sectionalization of the volumes defined bycylindrical chambers 20, 22 and 23 within engine 10 is accomplished bythe mutual coaction of rotors 30 and 50 and lobe 76 with the surfaces ofchambers 20, 22 and 23, the rotor surfaces and chamber surfaces shouldbe machined to provide as little clearance as possible. Clearances of0.001 inches or less are desirable. However, under certain enginedesigns, greater clearances may be tolerated.

With respect to the specific design of rotors 30 and 50, and of lobe 76,it can be seen that rotors 30 and 50 are identical, each being providedwith opposed arcuate peripheral surfaces and opposed relieved portions.The arcuate surfaces are provided to establish a sealing relationshipbetween the rotors and the surface of the cylindrical chambers so as toprevent the passage of gas between the rotor surface and the chambersurface during operation. Each arcuate surface may be of any lengthwhich is greater than the arcuate distance between edges 25 and 26defined by the intersections of chambers 20 and 23 so as to enablecomplete isolation of chamber 23 from chamber 20. The degree of reliefof the opposed relieved surfaces is dependent upon the desired volume ofgas to be worked and the desired compression ratio.

As is evident from F 16. 1, although rotors 30 and 50 are identical,they are operationally positioned so as to have their correspondingdiagonals normal to one another. This relationship between the rotorsdefines the relationship between each of the rotors and lobe 76, thecross-section of which lobe defines a curve which is developed by therotation of rotors 30 and 50 and the criteria that at all times must thesurface of lobe 76 be in substantial line contact with the surface ofeach of rotors 30 and 50. As was noted above, lobe 76 rotates in thesame direction as rotors 30 and 50 but at twice the angular velocity.-Thus, each of the relieved portions of rotors 30 and 50 are accommodatedto have continuing substantial surface-to-surface line contact with thesurface of lobe 76 and an effective fluid seal from one side to theother side of the lobe is maintained at all times.

Considering now the operation of engine 10, FIGS. through 10 presentschematically a complete cycle of the engine which is described below indetail. Referring to FIG. 5, it can be seen that rotor 30 has a firstrelieved surface 162 and a second relieved surface 163, and similarlythat rotor 50 has a first relieved surface 165 and a second relievedsurface 166. First relieved surface 162 of rotor 30 cooperates with thesurface of upper cylindrical chamber to define a first working volume168. Second relieved surface 163 of rotor 30 also cooperates with thesurface of upper cylindrical chamber 20 to define a second workingvolume 169. The arcuate surface of rotor 30 cooperates with firstrelieved surface 165 of rotor 50, the surface of lower cylindricalchamber 22 and lobe 76 to define third and fourth working volumes 170and 171 respectively. Finally, the second relieved surface 166 of rotor50 cooperates with the surface of lower cylindrical chamber 22 to definea fifth working volume 172.

The positions of the rotors in FIG. 5 indicate that rotor 30 has justbecome positioned adjacent longitudinally extending edge 25 to establisha seal between third working volume 170 and first working volume 168.With engine 10 in operation and with the rotors positioned as shown inFIG. 5, first working chamber 168 is being exhausted through bore 117,second working chamber 169 is receiving a properly prepared mixture offuel and air through bore 116, third working volume 170 has been filledwith a charge of combustible fluid and is reducing in size during thecompression stage of the cycle, fourth working volume 171 is shown atthe substantial completion of an expansion stage and fifth workingvolume 172 is in the process of being substantially evacuated prior tocoming into communication with inlet mixture bore 124. In this regard,it should be noted that as rotors and pass divider strips 133 and 141respectively, residual exhaust gases which otherwise be trapped behindthe divider strips are relieved to exhaust bores 117 and 128 throughchannels 137 and respectively.

Referring to FIG. 6, it can be seen that the rotors have rotated a fewdegrees more clockwise and rotor 50 is positioned such that firstrelieved surface thereof has advanced to a point adjacent exhaust bore128 thus marking the completion of the expansion cycle for fourthworking chamber 171. In this regard, it should be noted that the arcuatesurface of rotor 30 is still positioned substantially adjacent secondlongitudinally extending edge 26 so as to establish a sealingrelationship therewith and prevent the communication of gas betweensecomd working volume 169 and fourth working volume 171. This, combinedwith the fact that exhaust bore 128 is of larger size than inlet bore116 permits the relief of pressure within fourth working volume 171prior to communication thereof through second working volume 169 withinlet bore 116 so as to prevent a backfire of the apparatus throughinlet bore 116.

With respect to the remaining working volumes as shown in FIG. 6, firstworking volume 168 is continuing to be exhausted through exhaust bore117, third working volume is continuing to diminish in size whereby tocompress the combustible mixture contained therein, and fifth workingvolume 172 is substantially completely evacuated. In this regard, itshould be noted that evacuation in accordance with the present inventionis accomplished by the cooperation of divider strips 133 and 141 withthe surfaces of rotors 30 and 50, respectively. More specifically,referring to FIGS. 5 and 6, as rotor 51 turns clockwise within lowercylindrical chamber 22, exhaust gases between divider strip 141 andexhaust bore 128 are prevented from passing divider strip 141 by thesubstantially surface-tosurface contact between divider strip 141 andthe surface of rotor 50. Thus, as rotor 50 continues to rotateclockwise, the volume of fifth working volume 172 becomes greaterthereby causing a vacuum to be induced therein. Ultimately, thisevacuated space will communicate with a source of combustible gasthrough inlet bore 124 and because of the preestablished vacuum therein,the intake of fuel mixture into the engine will be expedited.

As the engine rotors rotate from the positions shown in FIG. 6 to theposition shown in FIG. 7, it can be seen initially with respect to firstworking volume 168 that exhaust of expended gases therefrom iscontinuing. Second and fourth working volumes 169 and 171 have beenplaced in communication and thus, a unidirectional flow of gas isestablished from inlet bore 116 through working volumes 169 and 171 andout exhaust bore 128. This unidirectional flow facilitates the removalof all spent gases from the apparatus thereby improving the efficiencyof the engine and its capability for clean running. By comparison, thirdworking volume 170 has diminished to its maximum compression point andat substantially this time the compressed fuel mixture is ignited andexpansion commences. Concurrently, fifth working volume 172 has comeinto communication with inlet bore 124 thereby facilitating the intakeof fuel mixture through bore 124.

As the rotation of the rotors continues from the positions shown in FIG.7 to the positions shown in FIG. 8, it can be seen that first workingvolume 168 leaves communication with exhaust bore 117 and is in theprocess of being evacuated by the cooperation of divider strip 133 withrelieved surface 162 in the manner discussed above with respect to fifthworking volume 172. Additionally, the arcuate surface of rotor 50 hascome into sealing position with respect to fourth longitudinallyextending edge 28 thereby isolating second working volume 169 fromfourth working volume 171 and commencing the compression stage of thecycle for second working volume 169. Third working volume 170 continuesin the expansion stage of the cycle, fourth working volume 171 continuesin the exhaust stage of the cycle, and fifth working volume 172continues in the intake stage of the cycle.

Still continued rotation of the rotors from the positions shown in FIG.8 to the positions shown in FIG. 9 causes first working volume 168 to becontinued to be evacuated by the cooperation of divider strip 133 andsurface-to-surface engagement with the first relieved surface 162 ofrotor 30.

Second working volume 169 continues in its compression stage of thecycle while third working volume 170 is just completing the expansionstage of its cycle and commencing the exhaust stage. In this regard, itshould be noted again that exhaust bore 117 is sized or positioned insuch a manner as to permit the communication of third working volume 170with exhaust bore 117 prior to the communication of third working volume170 with fifth working volume 172 as continued rotation of the rotorstakes place. This precommunication of third working volume 170 withexhaust bore 117 permits the relief of gaseous pressure from thirdworking volume 170 and prevents backfire as discussed above. Finally,fourth working volume 171 continues in its exhaust stage.

Rotation of the rotors from the positions shown in FIG. 9 to thepositions shown in FIG. 16 causes a full communication between third andfifth working volumes 170 and 172 so as to generate a flow of fluidthrough inlet bore 124, fifth working volume 172 and third workingvolume 170 out of exhaust bore 117 whereby to urge these volumes ofengine 111 of all spent gases. First working volume 168 has justfinished complete evacuation and is coming into communication with inletbore 116 whereby to be charged with fuel. Second working volume 169 isapproaching its fully compressed state and is ready for ignition andfourth working volume 171 is continuing in the exhaust stage of itscycle.

It can be seen from the foregoing, therefore, that for each completerotation of rotors 30 and 50, four full power strokes occur.Additionally, the efficiency of the combustion is relatively highbecause of the purging action of the unilateral flow of intake andexhaust gases which occurs when adjacent working volumes are incommunication through intermediate cylindrical chamber 23. In thisregard, it will be recognized by those skilled in the art that thisengine is typical of most rotary engines and operates at very highspeeds. Thus, although the operation of the engine has been described ina step-by-step fashion, it will be recognized that each of the stepsoccurs in a very short period of time and thus loses its individualityto contribute to the smoothly flowing operation of the engine.

A second embodiment of engine according to the invention is shownschematically in FIGS. 11 through 14. This embodiment is substantiallythe same in construction as the embodiment discussed above with respectto FIGS. 140, except for the fact that the engine, designated generallyby the reference numeral 211 is provided with three major rotors ratherthan the two dis closed with respect to the prior embodiment.

Considering engine 210 in detail, therefore, and with reference to FIGS.11-14 which show engine 210 schematically, an engine block 216 is shownto be provided with first, second and third longitudinally, coaxiallyextending cylindrical chambers 220, 221 and 222, respectively. Thelongitudinal axis of chambers 2211, 221 and 222 are symmetrically spacedabout the central longitudinal axis of block 216 which defines thelongitudinal axis of an intermediate longitudinally extendingcylindrical chamber 223 which is in communication with each of chambers220, 221 and 222.

The inner section of first chamber 220 with intermediate chamber 223defines first and second longitudinally extending edges 225 and 226.Similarly, the inner section of second and third cylindrical chambers221 and 222 define third, fourth, fifth and sixth longitudinallyextending edges 227-231), respectively.

Operably disposed within each of cylindrical chambers 221), 221 and 222are first, second and third rotors 232, 233 and 234 each respectiverotor being rigidly mounted for rotation on the shafts 236, 238 and 240.

Operably disposed within intermediate cylinder 223 is a two lobe rotaryvalve 246 which is rigidly secured such as by keying to a shaft 248. Thelongitudinal axis of shaft 246 is parallel with the longitudinal axes ofrotors 232, 233 and 234.

Each of cylindrical chambers 220, 221 and 222 is provided with an inletbore, 250, 251 and 252 respectively, which is connected to a fuel linein communication with a suitable source of combustible mixtures such asa carburetor (not shown). Similarly, each of cylindrical chambers 220,221 and 222 is provided with an exhaust bore, 255, 256 and 257respectively, which is in communication with a suitable exhaust system(not shown).

In the same manner as discussed above with respect to the-embodiment ofFIGS. 1-10, each of cylindrical chambers 2211, 221 and 222 is providedwith a longitudinally extending slot for receiving'a spring loadeddivider strip, the strips being shown in FIGS. 11-14 as 259, 2611 and261 respectively. The surfaces of chambers 220, 221 and 222 are eachprovided with a channel 276, 277 and 278 respectively, which communicatethe strip-containing slots with exhaust bores 255, 256 and 257.Additionally,'suitable bores are provided in block 216 to accommodatethe mounting therein of spark plugs 263, 264 and 265 which are operablyconnected to a suitable source of ignition energy such as a distributor.

Although the embodiment of engine shown in FIGS. 11-14 is shown onlyschematically, it will be recognized by those skilled in the art thatthe engine may be structured in the basic manner discussed above with respect to the embodiment of FIGS. 1-10. More specifically, an engine 210would be provided with end block sections or their equivalent, bearingmeans for rotatably supporting the shafts, gear means or the like forinterconnecting the rotors and the centrally disposed rotary valve,starter means, ignition means, means for connecting the engine to a loadsuch as a splined output shaft and means for cooling the engine duringoperation. The only basic difference is that the means for interlockingthe rotors and the shaft 248 of the rotary valve would be gear means orthe like sized to provide rotation of valve 246 at twice the speed ofeach of rotors 232, 233 and 23 1-.

Considering now the operating cycle of the threerotor engine 210, it canbe seen from the FIGS. that the rotors 232, 233 and 234 and valve 246cooperate with the longitudinally extending cylindrical chambers 220,221, 222 and 223 to form working volumes in the same manner as wasdiscussed above with respect to the embodiment of FIGS. 1-10. In thisregard, the operation of this embodiment of the engine is substantiallythe same as discussed with respect to the embodiment of FIGS. 1-10 withthe exception that there is one additional primary rotor. Thus,considering the operation of the engine in terms of a single workingcycle and referring to FIG. 11, a first relieved surface 268 of rotor232 cooperates with the inner surface of chamber 220 to define a workingvolume 2711. Similarly, the surfaces of rotors 232 and 233 cooperatewith the surface of valve 246 and the surface of intermediate chamber223 to define a second working volume 272. In the stage of the cycleshown in FIG. 11, the arcuate surface of rotor 232 is in close proximityto longitudinally extending edge 226 thereby establishing a seal forpreventing the flow of gases between first working volume 270 and illsecond working volume 272. First working volume 270 is in communicationwith intake bore 250 and is filled to capacity with a combustiblemixture of fuel and air. Continued rotation of the rotors from thepositions shown in FIG. 11 to the positions shown in FIG. 12 causescommunication of first working volume 270 with second working volume272. The establishment of this communication marks the commencement ofthe compression stage of the engine cycle which continues as the rotorsrotate through the positions shown in FIG. 13 to the positions shown inFIG. 14, whereupon spark plug 264 ignites the mixture to commence theexpansion or power stage of the cycle.

The surfaces of rotor 233, cylindrical chamber 221 and lobe 246cooperate to define a third working volume 274 (FIG. 14) in which theexpansion of the ignited gases takes place. This expansion continuesuntil rotor 233 has rotated sufficiently to place third working volume274 in communication with exhaust bore 256 thus relieving the ventexhaust gases to the exhaust system. Still further rotation of rotor 233causes third working volume 274 to pass by divider strip 260 whereby tocreate a vacuum therein in preparation for being placed in communicationwith inlet bore 251 to repeat the cycle once again.

The combustion cycle described above with respect to working chambers270, 272 and 274 is typical of the operation which continues throughouteach of the chambers of engine 210. Thus, it can be seen that thisoperation is substantially the same as that described above with respectto the embodiment of FIGS. 1-10 in that it provides the advantages ofuni-directional flow of gases through the engine and the attendantpurging capabilities and also provides for six expansion phases for eachsingle rotation of the main rotors.

Rotary engine 310 is exactly the same structurally as the embodimentdiscussed above in detail with respect to FIGS. 1-10 with twoexceptions, viz. each of the main rotors has a single relieved surfacerather than plural relieved surfaces and the rotary valve is geared torotate at the same angular speed as the main rotors rather than at twicethe speed as provided for in engine 10.

Considering the structure of engine 310 briefly, upper and lower mainrotors 312 and 314 are mounted on shafts 316 and 318 for rotation withinupper and lower longitudinally axially extending cylindrical chambers320 and 322, respectively. Cylindrical chambers 320 and 322 are incommunication through an intermediate longitudinally axially extendingcylindrical chamber 323, the longitudinal axis of which is parallel toand contained in the same plane as the longitudinal axis of chambers 320and 322. Mounted on an axially extending shaft 325 for rotation withinintermediate chamber 323 is rotary valve comprising a lobe 326, thesurface of which is configured to define a substantiallysurfaceto-surface line contact with the surfaces of each of rotors 312and 314 at all times during operation of the engine 310.

Cylindrical chambers 320, 322 and 323 are formed in a block member 336),it being understood that the complete engine 310 requires end blocks orequivalent closures when fully assembled. Also formed in block member330 are intake and exhaust bores 332, 333, 334 and 335, one intake andone in exhaust bore communicating with chambers 320 and 322.Additionally, block 330 is provided with longitudinally extending slots,one formed in the surface of each chamber 320 and 322, in which slotsare received spring loaded divider strips 338 and 339. The surfaces ofchambers 320 and 322 are each relieved to provide channels extendingbetween the respective slots for divider strips 338 and 339 and exhaustbores 334 and 335. Disposed in communication with intermediate chamber323 through suitable bores in block 330 are first and second ignitionmeans 342 and 343 which may be spark plugs or the like.

Considering now the operation of rotary engine 310, it can be seen fromFIG. 15 that upper rotor 312 is provided with a relieved surface 345which cooperates with the surface of upper cylindrical chamber 320 todefine a first working volume 346. Similarly, lower rotor 314 isprovided with a relieved surface 348 which cooperates with the surfacesof lower cylindrical chamber 322 the surfaces of intermediatecylindrical chamber 323 and the surface of valve 326 to define secondand third working volumes 348 and 350, respectively.

Because the combustion cycle in working volumes 346, 348 and 350 isexactly the same as that described above with respect to the workingvolumes of rotary engine 10, it suffices with respect to the detaileddescription of the operation of rotary engine 310 to describe the stagesof the combustion cycle in which each of the working volumes 346, 348and 350 appears in FIGS. 15-18. Thus, in FIG. 15, first working volume346 is substantially at the completion of its exhaust and evacuationstage, second working volume 348 is nearing the completion of itsexpansion stage and third working volume 350 is nearing the completionof its compression stage.

In FIG. 16, the rotors have rotated in a clockwise direction and firstworking volume 346 is shown during its intake stage, second workingvolume 348 is shown during its exhaust stage, and third working volume350 is shown at its substantially maximum compression point whichcorresponds approximately to the time of ignition. In this regard, itwill be recognized by those having skill in this art that the instant ofignition can be varied in accordance with the proper tuning of theengine.

In FIG. 17, the rotors have rotated an additional 90 clockwise from thepositions shown in FIG. 16 and first working volume 346 is shownimmediately after the completion of its intake phase and at thebeginning of its compression stage. Second working volume 348 is shownsubstantially at the completion of its exhaust and evacuation stages andthird working volume 350 is shown during its expansion stage. Finally,with respect .to FIG. 18, first working volume 346 is shown at thesubstantial completion of its compression stage, second working volume348 is shown during its intake stage and third working volume 350 isshown during its exhaust stage. It can be seen, therefore, that rotaryengine 310 is substantially the same engine as that discussed above withrespect to FIGS. 1-10 with the exception that rather than fourcombustion cycles for each full rotation of the rotors, there occursonly two.

The embodiment of rotary engine disclosed in FIGS. 19-22 and designatedgenerally by the reference numeral 410 is different from the priorembodiments because it has only a single major rotor. The basicconstruction of engine 410 is the same as that discussed above withrespect to the prior embodiments to the extent that similar end cover,bearings, gearing and carburetion and distributor arrangements may beutilized.

Considering the structure of engine 410 briefly, a block member 412 isprovided with a first longitudinally extending cylindrical chamber 414wherein is mounted a rotor 416 for rotation with a shaft 41%. Firstchamber 414 is in communication with a second longitudinally extendingcylindrical chamber 420 wherein there is mounted a three lobe rotaryvalve 422 for rotation with the shaft 424. Shafts 418 and 424 areconnected through external gearing (now shown) which is sized to providefor rotation of valve 422 at two thirds the speed of rotor 416. In thisregard, the crosssectional configuration of valve 422 is designed toprovide for substantial surface-to-surface line contact between thevalve lobes and rotor 416 at all times during the operation of engine410.

Formed in the upper surface of cylindrical chamber 420 is a relievedchannel 426 the function of which is discussed below with respect to theoperation of engine 414. Extending through the wall of block member 412is an intake bore 428 for communicating the interior of chamber 414 witha suitable source of combustible mixture, e.g. a carburetor, and anexhaust bore 430 which communicates the interior of chamber 414 with asuitable exhaust system for exhaust gases. Also formed in the surface ofchamber 414 is a longitudinally extending slot in which is mounted aspringloaded divider strip 432. In the same manner as was discussedabove with respect to the other embodiments, divider strip 432 is springloaded in such a manner as to be in surface-to-surface engagement withthe surface of rotor 416 at all times during operation of the engine410. Further, exhaust bore 430 and the seat containing divider strip 432are in communication through a channel formed in the surface of chamber414.

Ignition of the combustible mixture in engine 416) is accomplished by anignition means such as spark plug 443 which is electrically connected toa suitable source of energy such as a distributor or the like.

Considering therefore the operation of engine 410, it can be seen thatrotor 416 cooperates with the surface of chamber 414, the surface oflobe 422 and a portion of the surface of chamber 420 to define a firstworking volume 435 and a second working volume 437. Additionally, lobe422 cooperates with the inner surface of cylindrical chamber 429 todefine a third working volume 439 and a fourth working volume 441. As isevident from FIG. 19, working volumes 439 and 441 are in communicationthrough relieved channel 426.

Thus, referring to FIG. 19, first working volume 435 is in the intakestage of the combustion cycle, working volumes 439 and 441 are incommunication and in the high compression phase of the cycle just priorto ignition, and fourth working volume 437 is in the exhaust phase ofthe cycle. A rotor 416 and lobe 422 rotate from the positions shown inFIG. 19 to the positions shown in H6 20, fourth working volume 441becomes isolated from third working volume 439, and at approximatelythis point in the stage, spark plug 443 is actuated to ignite thecombustible mixture contained within working volume 441 and commence theexpansion phase of the combustion cycle. Additionally, the surface ofrotor 416 has covered intake bore 425, thus signifying the end of theintake stage of the combustion cycle for first working volume 435 andthe commencement of the compression stage. Similarly, second workingvolume 437 is completing the exhaust and evacuation stages of itscombustion cycle.

Continued rotation of rotor 416 and lobe 422 from the positions shown inFIGS. 20 to the positions shown in FIG. 21 causes further compression ofthe combustible mixture in first working chamber 435, places intake bore428 iii communication with second working volume 437 and continues withthe expansion stage of the cycle of fourth working volume 441. It shouldbe noted that during the period of rotation of lobe 422 between theposition shown in FIG. 20 and the position shown in FIG. 21, noparticular operation is being accomplished by or performed on thecombustible mixture contained within third working volume 439.

Continued rotation of rotor 416 and lobe 422 from the positions shown inFIG. 21 to the positions shown in FIG. 22 cause continued compression ofthe combustible mixture in first working volume 435, permit furtherintake of combustible mixture into second working volume 437, causes theexhaust bore 430 to be uncovered thereby terminating the expansionstageof the combustion cycle for the combustion products in fourthworking volume 441 and continues the movement of the combustible mixturein third working volume 439. The rotation of rotor 416 and lobe 422continues hereafter until the rotor and lobe positions as shown in FIG.19 are reached and the cycle continues in this manner.

Thus, it can be seen with respect to the embodiment of rotary engine 410that by properly controlling the speed of rotation of lobe 422 incojunction with the speed of rotation of rotor 416, the above describedad vantages of providing a continuous throughput of combustible gasesand a uni-directional flow of gases from the intake through the exhaustenables combustion a higher degree of efficiency and with bettercontrol.

A yet further embodiment of a rotary engine according to the presentinvention is disclosed in FIGS. 23-25 and designated generally byreference numeral 510. The construction of engine 510 is substantiallythe same as that discussed above with respect to rotary engine 414} withthe exception that the rotor of engine 510 is circular incross-sectional configuration and mounted for eccentric rotation and therotary valve lobe operates at one third of the angular velocity of themain rotor.

Considering the structure of engine 510 briefly, a block number 512 isprovided with a first longitudinally extending cylindrical chamber 514wherein is mounted a rotor 516 for rotation on a shaft 518. Firstchamber 514 is in communication with a second longitudinally extendingcylindrical chamber 520 wherein there is mounted a three lobe rotaryvalve 522 for rotation with a shaft 524. Shafts 518 and 524 areconnected through external gearing (not shown) which is sized to providefor rotation of valve 522 at one third the speed of rotor 516. In thisregard, the cross-sectional configuration of valve 522 is designed toprovide for substantial surfaceto-surface line contact between the lobesurfaces of valve 522 and rotor 516 at all times during operation or"the engine 5141.

Formed in the upper surface of cylindrical chamber 520 is a relievedchannel 526 the function of which is discussed below with respect to theoperation of this engine. Extending through the wall of block member 5X2is an intake bore 523 for communicating the interior of chamber 514 witha suitable source of combustible mixture, e.g. a carburetor, and anexhaust bore 530 which communicate the interior of chamber 514 with asuitable exhaust system for exhaust gases. Also formed in the surface ofchamber 514 between intake bore 528 and exhaust bore 530 is alongitudinally extending slot in which is mounted a spring loadeddivider strip 532. In the same manner as was discussed above withrespect to the prior described embodiments, divider strip 532 is springloaded in such a manner as to be in surface-to-surface engagement withthe surface of rotor 516 at all times during the operation of engine516. Further, exhaust bore 530 and the slot containing divider strip 532are in communication through a channel 533 formed in the surface ofchamber 514.

A bore is formed in the wall of block member 512 to be in communicationwith the interior of second chamber 520 and to provide for the mountingtherein of a suitable ignition means such as a spark plug 543. Thepositioning of spark plug 543 should be angularly spaced clockwise fromrelieved channel 526 so as to permit the timing of ignition at a pointin the cycle which is subsequent to the passage of the apex of a lobe ofvalve 522 to preclude the promulgation of combustion in acounterclockwise direction.

Considering therefore the operation of rotary engine 510, it can be seenfrom FIGS. 23-25 that rotor 516 and valve 522 cooperate with the innersurfaces of Iongitudinally extending cylindrical chambers 514 and 520 todefine first, second and third working volumes 535, 537 and 539respectively. With particular reference to FIG. 23, first working volume535 has one portion in the intake phase of the combustion cycle andanother portion, i.e. that portion disposed counter-clockwise fromdivider strip 532 in the exhaust phase of the combustion cycle. Secondworking volume 537 is in communication with third working volume 539through channel 526 to provide compressed combustion gases to thirdworking volume 539 just prior to ignition which occurs selectively afterthe apex of a lobe of valve 522 passes the clockwise edge of channel 526as seen in FIG. 23. Rotation of the valve and rotor from the positionsshown in FIG 23 to the positions shown in FIG. 24 causes rotor 516 tocover exhaust bore 530 thus marking the completion of the exhaust phasefor first working volume 535 except for that portion of the spent gaseswhich flow through channel 533 from the area of divider strip 532 toexhaust bore 530, causes second working volume 537 to be isolated fromthird working volume 539 by the sealing action of the apex of valve 522with the inner surface of cylindrical chamber 520 and places thirdworking volume 539 into the expansion phase of the combustion cycle.

The continued rotation of lobe 522 and rotor 516 from the positionsshown in FIG. 24 to the positions shown in FIG. 25 causes the coveringof intake bore 528 thereby completing the intake stage of the combustioncycle for first working volume 535, causes clockwise displacement ofsecond working volume 537 in anticipation of its communication withfirst working volume 535 for purposes of preparing for ignition anduncovers exhaust bore 530 to commence the exhaust stage of thecombustion cycle for working volume 539.

Rotary engine 510 thus provides in a rotary engine of the eccentricrotor type the advantage of unidirectional flow of gases through theengine from the intake to the exhaust stages of the combustion cycle. Aswill be recognized by those skilled in this art, the imbalance createdby a single eccentric rotor can be offset by providing an additionalengine stage with the rotor disposed it??? out of phase with rotor 516.Similarly, plural additional stages or opposed counterweight can beutilized to accomplish the same balancing effect.

It will also be recognized by those skilled in the art that although thedisclosed embodiments have been charged with combustion materialsthrough a carburetion means, other combustion material chargingapproaches may be utilized, e.g. fuel injection.

The above described embodiments of rotary engines will be recognized asproviding a rotary engine design which is unique, which providesadvantages over prior art devices and which, because of the eliminationof undercuts and the like in the engine members provides for economicand speedy manufacture.

Although five embodiments of rotary engines according to the inventionhave been disclosed in detail above, it is considered to be manifestthat many modifications thereto can be made without departing from thespirit and scope of this invention.

I claim:

1. A rotary internal combustion engine comprising:

a block;

a first longitudinally extending cylindrical chamber formed in saidblock;

a second longitudinally extending cylindrical chamber formed in saidblock, the longitudinal axis of said second chamber being parallel toand spaced from the longitudinal axis of said first chamber;

a third longitudinally extending chamber formed in said block, thelongitudinal axis of said third chamber being parallel to and disposedcentrally of the longitudinal axes of said first and second chambers,said axes of said first and second chambers being disposed symmetricallyabout said axis of said third chamber and equidistant therefrom, saidthird chamber having a diameter to overlap said first and secondchambers for placing said first, second and third chambers in mutualcommunication;

a first rotor operably co-axially disposed within said first chamber,said first rotor comprising a generally cylindrical member having adiameter substantially equal to the inside diameter of said firstchamber, and at least one relieved portion on the surface thereof forcooperating with at least said first chamber to define a working volume;

a second rotor operably co-axially disposed within said second chamber,said second rotor comprising a generally cylindrical member having adiameter substantially equal to the inside diameter of said secondchamber, and at least one relieved portion on the surface thereof forcooperating with at least said second chamber to define a workingvolume;

said first and second rotors operationally positioned in said first andsecond chambers with the axis of said relieved portions thereofsubstantially normal to each other;

a third rotor operably co-axially disposed within said third chamber,said third rotor comprising a lobe member, said lobe member defining asurface for providing a substantial surface-to-surface line contact withthe surfaces of said first and second rotors at all times duringrotation of said rotors;

intake means for introducing a charge of combustible material into atleast one of said first and and second chambers;

exhaust means for exhausting combustion products from at least one ofsaid first and second chambers;

ignition means for igniting said combustible material within said block;each said working volume, under the control of the rotation of saidfirst, second and third rotorsbeing efiectively displaced from being incommunication with said ignition means and thereafter to being incommunication with said exhaust means during the combustion cycle ofsaid rotary engine; and

means for interengaging said first, second and third rotors to controltheir relative rotation in the same rotational direction.

2. A rotary engine according to claim 1 and further including means forevacuating said working volumes after each has been in communicationwith said exhaust port and prior to each coming into communication withsaid inlet ports.

3. A rotary engine according to claim 2 wherein said means forevacuating cooperates with said rotatable means to force gases from saidworking volumes through said exhaust ports.

4. A rotary engine according to claim 1 wherein said block comprises atleast a first end element, a second end element and at least onecentralelement, and said longitudinally extending cylindrical chambers areformed in said central element.

5. A rotary engine according to claim 4 wherein said intake and exhaustports comprise passages extending through the wall of said centralelement into at least one of said chambers.

6. A rotary engine according to claim 2 wherein said means forevacuating said working volumes comprises a longitudinally extendingslot formed in the surface of said at least one of said cylindricalchambers, a divider strip reciprocably received within said slot, andmeans for resiliently urging said divider strip into surface-tosurfaceengagement with the rotatable means in said at least one of saidcylindrical chambers.

7. A rotary internal combustion engine comprising:

a block;

a first longitudinally extending cylindrical chamber formed in saidblock;

a second longitudinally extending cylindrical chamber formed in saidblock, the longitudinal axis of said second chamber being parallel toand spaced from the longitudinal axis of said first chamber;

a third longitudinally extending cylindrical chamber formed in saidblock, the longitudinal axis of said third chamber being parallel to anddisposed between tlte longitudinal axis of said first and secondchambers, said third chamber being disposed between and overlapping saidfirst and second chambers in mutual communication;

a first rotor operably co-axially disposed within said first chamber,said first rotor comprising a generally cylindrical member having adiameter substantially equal to the inside diameter of said firstchamber, and at least one relieved portion on the surface thereof todefine a working volume;

a second rotor operably co-axially disposed within said second chamber,said second rotor comprising a generally cylindrical member having adiameter substantially equal to the inside diameter of said secondchamber, and at least one relieved portion on the surface thereof todefine a working volume;

a third rotor operably co-axially disposed within said third chamber,said third rotor comprising a lobe member defining a surface forproviding a substantial surface-to surface line contact with thesurfaces of both said first and second rotors at all times during therotation of said rotors;

intake means for introducing a combustible mixture into at least one ofsaid first and second chambers;

exhaust means for exhausting combustion products from at least the otherof said first and second chambers;

ignition means for igniting said combustible mixture within said block;means for interengaging said first, second and third rotors to controltheir relative rotation in the same rotational direction; v means forattaching said rotors to a means to be driven; and

means controlled by said first and second rotors and formed in saidblocks for evacuating said working volumes after each has been incommunication with said exhaust means and prior to each coming intocommunication with said intake means.

8. A rotary internal combustion engine according to claim 7 wherein saidblock comprises a first end element, a second end element and at leastone central element, and wherein said first, second and thirdlongitudinally extending cylindrical chambers are formed in said atleast one central element.

9. A rotary internal combustion engine according to claim 7 wherein saidintake means and said exhaust means comprise passages extending throughsaid block into said first and second chambers.

10. A rotary internal combustion engine according to claim g whereinsaid intake means and said exhaust means comprise passages formed insaid central element of said block and extending into said first andsecond chambers.

l l. A rotary engine according to claim 7 wherein said means forevacuating cooperates with said rotors to force gases from said workingvolumes through said exhaust means.

12. A rotary internal combustion engine according to claim 7 whereinsaid means for evacuating comprises:

face-to-surface engagement with the rotor in: said one of said first andsecond chambers.

13. A rotary internal combustion engine according to claim 7 whereinsaid ignition means is disposed toinitiate combustion of saidcombustible vapor within said third chamber.

1. A rotary internal combustion engine comprising: a block; a firstlongitudinally extending cylindrical chamber formed in said block; asecond longitudinally extending cylindrical chamber formed in saidblock, the longitudinal axis of said second chamber being parallel toand spaced from the longitudinal axis of said first chamber; a thirdlongitudinally extending chamber formed in said block, the longitudinalaxis of said third chamber being parallel to and disposed centrally ofthe longitudinal axes of said first and second chambers, said axes ofsaid first and second chambers being disposed symmetrically about saidaxis of said third chamber and equidistant therefrom, said third chamberhaving a diameter to overlap said first and second chambers for placingsaid first, second and third chambers in mutual communication; a firstrotor operably co-axially disposed within said first chamber, said firstrotor comprising a generally cylindrical member having a diametersubstantially equal to the inside diameter of said first chamber, and atleast one relieved portion on the surface thereof for cooperating withat least said first chamber to define a working volume; a second rotoroperably co-axially disposed within said second chamber, said secondrotor comprising a generally cylindrical member having a diametErsubstantially equal to the inside diameter of said second chamber, andat least one relieved portion on the surface thereof for cooperatingwith at least said second chamber to define a working volume; said firstand second rotors operationally positioned in said first and secondchambers with the axis of said relieved portions thereof substantiallynormal to each other; a third rotor operably co-axially disposed withinsaid third chamber, said third rotor comprising a lobe member, said lobemember defining a surface for providing a substantial surfaceto-surfaceline contact with the surfaces of said first and second rotors at alltimes during rotation of said rotors; intake means for introducing acharge of combustible material into at least one of said first and andsecond chambers; exhaust means for exhausting combustion products fromat least one of said first and second chambers; ignition means forigniting said combustible material within said block; each said workingvolume, under the control of the rotation of said first, second andthird rotors being effectively displaced from being in communicationwith said ignition means and thereafter to being in communication withsaid exhaust means during the combustion cycle of said rotary engine;and means for interengaging said first, second and third rotors tocontrol their relative rotation in the same rotational direction.
 2. Arotary engine according to claim 1 and further including means forevacuating said working volumes after each has been in communicationwith said exhaust port and prior to each coming into communication withsaid inlet ports.
 3. A rotary engine according to claim 2 wherein saidmeans for evacuating cooperates with said rotatable means to force gasesfrom said working volumes through said exhaust ports.
 4. A rotary engineaccording to claim 1 wherein said block comprises at least a first endelement, a second end element and at least one central element, and saidlongitudinally extending cylindrical chambers are formed in said centralelement.
 5. A rotary engine according to claim 4 wherein said intake andexhaust ports comprise passages extending through the wall of saidcentral element into at least one of said chambers.
 6. A rotary engineaccording to claim 2 wherein said means for evacuating said workingvolumes comprises a longitudinally extending slot formed in the surfaceof said at least one of said cylindrical chambers, a divider stripreciprocably received within said slot, and means for resiliently urgingsaid divider strip into surface-to-surface engagement with the rotatablemeans in said at least one of said cylindrical chambers.
 7. A rotaryinternal combustion engine comprising: a block; a first longitudinallyextending cylindrical chamber formed in said block; a secondlongitudinally extending cylindrical chamber formed in said block, thelongitudinal axis of said second chamber being parallel to and spacedfrom the longitudinal axis of said first chamber; a third longitudinallyextending cylindrical chamber formed in said block, the longitudinalaxis of said third chamber being parallel to and disposed between thelongitudinal axis of said first and second chambers, said third chamberbeing disposed between and overlapping said first and second chambers inmutual communication; a first rotor operably co-axially disposed withinsaid first chamber, said first rotor comprising a generally cylindricalmember having a diameter substantially equal to the inside diameter ofsaid first chamber, and at least one relieved portion on the surfacethereof to define a working volume; a second rotor operably co-axiallydisposed within said second chamber, said second rotor comprising agenerally cylindrical member having a diameter substantially equal tothe inside diameter of said second chamber, and at least one relievedportion on the surface thereof to define a working volume; a third rotoroperably co-axiallY disposed within said third chamber, said third rotorcomprising a lobe member defining a surface for providing a substantialsurface-to surface line contact with the surfaces of both said first andsecond rotors at all times during the rotation of said rotors; intakemeans for introducing a combustible mixture into at least one of saidfirst and second chambers; exhaust means for exhausting combustionproducts from at least the other of said first and second chambers;ignition means for igniting said combustible mixture within said block;means for interengaging said first, second and third rotors to controltheir relative rotation in the same rotational direction; means forattaching said rotors to a means to be driven; and means controlled bysaid first and second rotors and formed in said blocks for evacuatingsaid working volumes after each has been in communication with saidexhaust means and prior to each coming into communication with saidintake means.
 8. A rotary internal combustion engine according to claim7 wherein said block comprises a first end element, a second end elementand at least one central element, and wherein said first, second andthird longitudinally extending cylindrical chambers are formed in saidat least one central element.
 9. A rotary internal combustion engineaccording to claim 7 wherein said intake means and said exhaust meanscomprise passages extending through said block into said first andsecond chambers.
 10. A rotary internal combustion engine according toclaim 8 wherein said intake means and said exhaust means comprisepassages formed in said central element of said block and extending intosaid first and second chambers.
 11. A rotary engine according to claim 7wherein said means for evacuating cooperates with said rotors to forcegases from said working volumes through said exhaust means.
 12. A rotaryinternal combustion engine according to claim 7 wherein said means forevacuating comprises: a longitudinally extending slot formed in thesurface of said at least the other of said first and second chambers; adivider strip reciprocably received within said slot; and means forresiliently urging said divider strip into surface-to-surface engagementwith the rotor in said one of said first and second chambers.
 13. Arotary internal combustion engine according to claim 7 wherein saidignition means is disposed to initiate combustion of said combustiblevapor within said third chamber.
 14. A rotary internal combustion engineaccording to claim 9 wherein said passages defining said intake meansand said exhaust means are covered and uncovered by said first andsecond rotors during their rotation within said first and secondchambers, respectively, said covering and uncovering of said passagesdefining a valving operation.
 15. A rotary internal combustion engineaccording to claim 7 wherein said first, second and third rotors areshaped such that tangents to the surfaces of the rotors along theirlines of substantial contact do not intersect the structure of thecontacting rotors. second and third rotors cooperate with said first,second and third longitudinally extending cylindrical chambers to defineworking volumes, said working volumes being effectively displaced frombeing in communication with said passage defining said intake means tobeing in communication with said ignition means and thereafter to beingin communication with said passage defining said exhaust means duringeach combustion cycle of said rotary engine.
 16. A rotary internalcombustion engine according to claim 7 wherein no tangent to the surfaceof any of said first, second or third rotors intersects the structure ofthe rotor to which it is tangent.
 17. A rotary internal combustionengine according to claim 7 wherein said relieved portion on thesurfaces of said first,
 18. A rotary internal combustion enginecomprising: a block; a first longitudinally extending cylindRicalchamber formed in said block; a second longitudinally extendingcylindrical chamber formed in said block, the longitudinal axis of saidsecond chamber being parallel to and spaced from the longitudinal axisof said first chamber; a third longitudinally extending cylindricalchamber formed in said block, the longitudinal axis of said thirdchamber being parallel to and spaced from the longitudinal axes of saidfirst and second chambers; a fourth longitudinally extending chamberformed in said block, the longitudinal axis of said fourth chamber beingparallel to and disposed centrally of the longitudinal axes of saidfirst, second and third chambers, said axes of said second and thirdchambers being disposed symmetrically about said axis of said fourthchamber and equidistant therefrom, said fourth chamber beingsufficiently large in diameter to overlap said first, second and thirdchambers for placing said first, second, third and fourth chambers inmutual communication; a first rotor operably co-axially disposed withinsaid first chamber, said first rotor comprising a generally cylindricalmember having a diameter substantially equal to the inside diameter ofsaid first chamber, and at least one relieved portion on the surfacethereof for cooperating with at least said first chamber to define aworking volume; a second rotor operably co-axially disposed within saidsecond chamber, said second rotor comprising a generally cylindricalmember having a diameter substantially equal to the inside diameter ofsaid second chamber, and at least one relieved portion on the surfacethereof for cooperating with at least said second chamber to define aworking volume; a third rotor operably co-axially disposed within saidthird chamber, said third rotor comprising a generally cylindricalmember having a diameter substantially equal to the inside diameter ofsaid third chamber, and at least one relieved portion on the surfacethereof for cooperating with at least said third chamber to define aworking volume; a fourth rotor operably co-axially disposed within saidfourth chamber, said fourth rotor comprising a lobe member rigidlymounted on a shaft for rotation therewith, said lobe member defining asurface for providing a substantial surface-to-surface line contact withthe surfaces of said first, second and third rotors at all times duringthe rotation of said rotors; intake means for introducing a charge ofcombustible material into at least one of said first, second and thirdchambers; exhaust means from exhausting combustion products from atleast one of said first, second and third chambers; ignition means forigniting said combustible material within said block; each said workingvolume being effectively displaced from being in communication with saidintake means to being in communication with said ignition means andthereafter to being in communication with said exhaust means during thecombustion cycle of said rotary engine; means for interengaging saidfirst, second, third and fourth rotors to control their relativerotation; and means for attaching said rotors to a means to be driven.19. A rotary internal combustion engine according to claim 18 whereinsaid intake means and said exhaust means comprise passages extendingthrough said block into said first, second and third chambers.
 20. Arotary internal combustion engine according to claim 19 wherein saidignition means is disposed to initiate combustion of said combustiblemixture within said fourth chamber.
 21. A rotary internal combustionengine according to claim 19 wherein said passages defining said intakemeans and said exhaust means are covered and uncovered by said first,second and third rotors during their rotation within said first, second,and third chambers, respectively, said covering and uncovering of saidpassages defining a valving operation.
 22. A rotary engine according toclaim 18 and further including means for evacuating said woRking volumesafter each has been in communication with said exhaust port and prior toeach coming into communication with said inlet ports.
 23. A rotaryengine according to claim 22 wherein said means for evacuatingcooperates with said rotatable means to force gases from said workingvolumes through said exhaust ports.
 24. A rotary engine according toclaim 22 wherein said means for evacuating said working volumescomprises a longitudinally extending slot formed in the surface of saidat least one of said cylindrical chambers, a divider strip reciprocablyreceived within said slot, and means for resiliently urging said dividerstrip into surface-to-surface engagement with the rotatable means insaid at least one of said cylindrical chambers.
 25. A rotary expansiblechamber device comprising a block, at least one intake and at least onedischarge port formed in said block, a plurality of longitudinallyextending substantially cylindrical rotor chambers formed in said block,at least one longitudinally extending communication chamber formed insaid block and having an opening between each of at least two of saidrotor chambers for mutual communication therebetween, the longitudinalaxes of said rotor and communication chambers being spaced in parallelrelation, a rotor operably disposed in each of said rotor chambers, eachsaid rotor comprising at least one cylindrical lobe member having adiameter substantially equal apart from minimal clearance to the insidediameter of a cylindrical part of said rotor chamber in which said eachrotor is disposed and at least one relieved portion on the surfacethereof for cooperating with at least said last mentioned rotor chamberto define a working volume, a rotary valve operably disposed in each ofsaid at least one communication chamber, said rotary valve having aperipheral surface in line-to-line contact apart from minimal clearancewith said peripheral surfaces of said rotors disposed in each of said atleast two rotor chambers, said line-to-line contact existingsubstantially throughout each revolution of said rotors, said rotors andeach said rotary valve rotating in the same rotational direction, eachsaid rotary valve rotating at a rotational speed other than less thanthe rotational speed of said rotors, and said at least one rotary valveand said rotors disposed in said at least two rotor chambers areoperationally phased such that at least one variable volume compressionchamber and at least one variable volume expansion chamber occursubstantially simultaneously during a part of each revolution of saidrotary valve, said each one of said variable volume compression orexpansion chamber is defined by a part of a peripheral surface of acylindrical lobe member of one of said last-mentioned rotors, a part ofa relieved portion of another of said last-mentioned rotors, a part ofthe peripheral surfaces of said last-mentioned rotary valve, inner wallsurfaces of said communication chamber in which said last mentionedrotary valve is disposed, and inner wall surfaces of said rotor chamberin in which said other rotor is disposed.
 26. The invention of claim 25wherein said lobe member of each one of said rotors has a surfaceextending peripherally for substantially covering a predeterminedportion of said opening between said communication chamber and saidchamber within which said one of said rotors is disposed.
 27. Theinvention of claim 25 wherein each said rotary valve is rotatable at thesame rotational speed as said rotors.
 28. The invention of claim 25wherein each said rotary valve is rotatable at twice the rotationalspeed of said rotors.
 29. The invention of claim 28 wherein each of saidrotors has two said relieved portions operationally disposed in saidblock with axes normal to two respective relieved portions of another ofsaid rotors.
 30. The invention of claim 25 further comprising intakemeans for introducing a combustible mixturE into at least one of saidchambers, ignition means for igniting said combustible material withinsaid block, and means controlled by said rotors and formed in said blockfor evacuating each said working volume after each has been incommunication with said discharge port and prior to each coming intocommunication with said intake port.
 31. The invention of claim 25wherein said inner wall surfaces of each of said chambers in which saidrotors are disposed comprises end surface segments contiguous to endsurface segments of inner wall surfaces of said communication chamberand at said opening for forming sealing surface edges for separatingsaid variable volume compression and expansion chambers.
 32. Theinvention of claim 31 wherein said sealing surface edges coact with saidperipherally extending surface of said lobe member of a respective oneof said rotors for sealing said variable volume compression andexpansion chambers during a covering of said opening between saidcommunication chamber and said rotor chamber in which saidlast-mentioned one of said rotors is disposed.
 33. The invention ofclaim 25 wherein said rotary valve comprises first and second sidesurfaces and further comprising circular plates fitted to said sidesurfaces of said rotary valve and disposed within said block.